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CN110520634A - Equipment for adjusting hydrodynamic machine - Google Patents

Equipment for adjusting hydrodynamic machine Download PDF

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Publication number
CN110520634A
CN110520634A CN201880021394.5A CN201880021394A CN110520634A CN 110520634 A CN110520634 A CN 110520634A CN 201880021394 A CN201880021394 A CN 201880021394A CN 110520634 A CN110520634 A CN 110520634A
Authority
CN
China
Prior art keywords
hydraulic cylinder
pump
route
valves
emergency cut
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201880021394.5A
Other languages
Chinese (zh)
Other versions
CN110520634B (en
Inventor
托马斯·策勒
鲁文·霍哈格
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Patent GmbH
Original Assignee
Voith Patent GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of CN110520634A publication Critical patent/CN110520634A/en
Application granted granted Critical
Publication of CN110520634B publication Critical patent/CN110520634B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/022—Installations or systems with accumulators used as an emergency power source, e.g. in case of pump failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31582—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/862—Control during or prevention of abnormal conditions the abnormal condition being electric or electronic failure
    • F15B2211/8623—Electric supply failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8755—Emergency shut-down

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

For adjusting hydrodynamic machine, such as turbine, pump or the equipment for pumping turbine using the constant displacement pump that can be driven of variable speed, the equipment includes the device for implementing emergency cut-off, the equipment is characterized by having less energy consumption and higher efficiency, while ensuring to meet all hydrodynamic machines and operation and safety-related requirement.

Description

Equipment for adjusting hydrodynamic machine
Technical field
The present invention relates to a kind of equipment for adjusting hydrodynamic machine, in particular for adjusting turbine, pump or pump turbine Equipment.
Background technique
For adjusting the traditional equipment of hydrodynamic machine as well known to the general prior art.Thus, for example DE 27 13 867 A1 are described this equipment (see Fig. 3), the equipment include pressure oil-source, hydraulic execution motor (hydraulic cylinder) and for pair For regulating and controlling the regulating valve that the energy of hydraulic cylinder carries out dosage.In general, pressure oil-source is for hydraulic under over-voltage The memory of medium.The memory must fill herein by pump, and be brought to and be maintained at required operating pressure.
In addition, a kind of directing vane for opening and closing hydrodynamic machine as known in 10 2,013 212 937 A1 of DE The equipment of piece, in the hydraulic constant displacement pump driven with wherein having used variable speed.In this text, this set is only disclosed Working method in standby principle.
Summary of the invention
The task of the present invention is to illustrate a kind of equipment for adjusting hydrodynamic machine to have used variable speed wherein Ground driving hydraulic constant displacement pump, and the equipment ensure in hydrodynamic machine for example when being executed between, emergency cut-off Can (namely when pumping failure), suitable for big hydraulic cylinder in terms of requirement.Compared with traditional equipment, according to this hair Bright solution is distinguished by with high energy efficiency, good environment compatibility, easy to maintain and small purchasing and transporting Row cost.
According to the present invention, which is solved by the feature with claim 1 for adjusting the equipment of hydrodynamic machine Certainly.The other advantageous design scheme of equipment according to the present invention is obtained by dependent claims.
Detailed description of the invention
Next solution according to the present invention is illustrated by attached drawing.Wherein in detail:
Fig. 1 shows the schematical structure of equipment according to the present invention.
Specific embodiment
It schematically shows in the illustration of FIG. 1 according to the present invention for adjusting the equipment of hydrodynamic machine Structure.The equipment includes the collection marked with appended drawing reference 1 and compensates container, the pump assembly marked with appended drawing reference 2, uses attached drawing Label 3 mark variable speed pump controller, with appended drawing reference 5 mark memory, with appended drawing reference 6 mark it is hydraulic Cylinder, the emergency cut-off solenoid valve marked with appended drawing reference 72, uses attached drawing at the emergency cut-off conversion saddle marked with appended drawing reference 71 Mark two of label 81 and 82 can release the check-valves ended, with two pilot valves of the mark of appended drawing reference 91 and 92, with attached Icon remember 10,11 and 12 mark three throttling elements, with appended drawing reference 14 mark check-valves, with appended drawing reference 20 mark can The solenoid valve of choosing, the two optional pressure limiting valves marked with appended drawing reference 30 and 31 and two marked with appended drawing reference 40 and 50 Optional interface.The arrow for being in 6 lower section of hydraulic cylinder shows the closing direction of hydraulic cylinder.
The liquid that hydraulic cylinder 6 may, for example, be directive wheel hydraulic cylinder or be regulated and controled for the impeller blade to hydrodynamic machine Cylinder pressure.This hydraulic cylinder usually requires that the hydraulic fluid of large volume in order to run.Hydraulic cylinder 6 can be made into synchronized cylinder, such as As specified by the second bar shown by a dotted line in Fig. 1.But hydraulic cylinder 6 also can be made into for close side and opening Side has the cylinder with differential effect of different volumes.
Pump assembly 2 includes two pumps with reversible conveying direction.In Fig. 1, two pumps are arranged in and device 3 are driven by pump On the axis of driving.However the design scheme in other structures is also possible, for example, pump passes through pump controller by driver 3 drive.Even thinkable to be, pump controller 3 includes the motor and frequency converter for each of two pumps.Further Description be related to embodiment shown in Fig. 1.In the position shown in FIG. 1 of emergency cut-off conversion saddle 71, pump is connect Mouth respectively with the control connection of hydraulic cylinder, so that one of them be made to pump to 6 side of hydraulic cylinder in a rotation direction of axis To conveying hydraulic fluid, and another pump receives the hydraulic fluid from hydraulic cylinder 6.In another rotation direction of axis then exactly On the contrary.Then, in Fig. 1, the interface (via the check-valves 82 that can release cut-off) on the right of the pump of lower section and beating for hydraulic cylinder 6 Side connection is opened, and the interface (via the check-valves 81 that can release cut-off) on the left side of the pump of top and the close side of hydraulic cylinder 6 connect It connects.Remaining interface of pump is directly connect with collection and compensation container 1 respectively.That is, in one of rotation side of axis Upwards, hydraulic fluid is pumped into the opening side of hydraulic cylinder 6 by the pump of lower section from collection and compensation container 1, and at the same time, Hydraulic fluid is pumped into collection and compensation container 1 by the pump of top from the close side of hydraulic cylinder 6.In another rotation direction of axis On, then volume flow is in turn.In the case where the delivered volume amount that two pump is equally big, which means that finally without hydraulic fluid Body flow in collection and compensation container 1 or extracts (synchronized cylinder that see below) from collecting and compensating container.In another kind In the case of, the difference conveying capacity only pumped is just sent in collection and compensation container 1 or extracts from the collection and compensation container (cylinder with differential effect that see below).Be respectively in this condition, check-valves 81 and 82 all be release cut-off (see below to operation The description of state).
If used pump has specified pressure and draws interface, preferred pressure interface always with hydraulic cylinder 6 Connection, and draw interface and connect with collecting and compensating container 1.
The axis of pump assembly 2 is driven by the pump controller 3 for the variable speed that can be run in both rotational directions.Pump controller 3 generally include the execution motor of electricity, it is by inverter supply.
The check-valves 81 and 82 that cut-off can be released is arranged in the connection line of hydraulic cylinder 6 and pump assembly 2 so that they Not having to be released from prevents the piston of hydraulic cylinder from moving in the state of cut-off, these can release the check-valves of cut-off respectively with its In pilot valve 91,92 connect.These pilot valves difference is connect (via valve 20 and 72) with memory 5.Pilot valve 91,92 It opens therefore the check-valves 81,82 for causing institute's subordinate is released from cut-off.The opening of pilot valve 91,92 passes through hydrodynamic machine (electric) adjuster causes, and mode is: so that these pilot valves are motivated.Wherein each pilot valve 91,92 can be by Dividually motivate.
Under " emergency cut-off " or " quick closedown " operating status, that is to say, that when emergency cut-off conversion saddle 71 is in When different from position shown in FIG. 1, memory 5 is connect with the close side of hydraulic cylinder 6.In addition, in the two operating statuses, It collects and compensation container 1 is connect with the opening side of hydraulic cylinder 6.The control of the state of saddle 71 is converted via urgent to emergency cut-off Solenoid valve 72 is closed to realize, which is in hydraulic between emergency cut-off conversion saddle 71 and memory 5 In route.Emergency cut-off solenoid valve 72 is also in the route between pilot valve 91,92 and memory 5.(by load on spring) Emergency cut-off solenoid valve 72 is in operation always by persistent excitation, as a result, shown in Fig. 1 at emergency cut-off conversion saddle 71 Position in, and pilot valve 91,92 is supplied with oil pressure (this is to say, check-valves 81,82 can be this by memory 5 Cut-off is released under state by pilot valve 91,92).
Emergency cut-off conversion saddle 71 is configured to, so that emergency cut-off conversion saddle in the position shown in figure 1 will pump The interface of the corresponding interface and hydraulic cylinder 6 of the pump of component 2 connects, and will collect and compensation container 1 and memory 5 with The de- connection of hydraulic cylinder, and in its other positions, by the pump of pump assembly 2 and the de- connection of hydraulic cylinder 6, and it will collect and compensate and hold Device 1 connects with opening side and connects memory 6 and the close side of hydraulic cylinder 6.It can be seen in fig. 1 that tight Anxious conversion saddle of closing is loaded with the pressure of memory 5 on two sides.Exist here, the pressure is applied to effective face thereon Select of different sizes on two sides.It is caused by face on right side is larger, if emergency cut-off solenoid valve 72 is motivated, then Emergency cut-off is converted saddle 71 and is just located in the position shown in figure 1.If emergency cut-off solenoid valve 72 is released from excitation, deposit Reservoir 5 and emergency cut-off conversion saddle 71 right side separate and emergency cut-off conversion saddle 71 due to be applied to left side on power And it is pushed in other positions.
Also referred to as the throttling element 10 of " basic throttling element " is located in the route connecting with the opening side of hydraulic cylinder 6, however It is still located on before emergency cut-off conversion saddle 71, that is to say, that with 6 direct neighbor of hydraulic cylinder.Throttling element 11, which will be located at, to be stored In the route that device 5 and the rest part of equipment connect.Throttling element 12 is located at emergency cut-off conversion saddle 71 and collects and mend It repays in the route between container 1.Here, in two throttling elements 11 or 12 one be considered as it is optional (referring to for emergency cut-off The embodiment of function).
In addition, being additionally provided with following route, wherein one is connected from pump assembly 2 to the route of hydraulic cylinder 6 and memory 5 It picks up and.In the route, check-valves 14 is arranged so that the hydraulic fluid not from memory 5 can pass through.Fig. 1 is shown Only one in multiple possible alternatives, that is to say, that show the route with check-valves 14 for the pump of top The case where corresponding interface and memory 5 connect.Route with check-valves 14 can also be corresponding with the pump of lower section Interface connection.For this purpose, the route with check-valves 14 may be that this is leading to any of the route of hydraulic cylinder 6 from pump assembly 2 It is passed through on point.
Optionally, equipment can also include other emergency cut-off control valve (such as overspeed valve etc.).These are other Emergency cut-off control valve can be connected via interface 50, which is located at the hydraulic route where emergency cut-off solenoid valve 72 In.
It is alternatively possible to which other customer is attached to memory 5 via interface 40.Interface 40 is located at memory 5 In the hydraulic route connected with remaining equipment.
The equipment according to the present invention in each operating status in hydrodynamic machine is illustrated in more detail below Working method, and the advantages of illustrate the equipment.In this, it is assumed that being initial state, memory 5 is charged to limit Pressure, and hydraulic cylinder 6 is in arbitrary middle position.
The adjusting of hydrodynamic machine is run:
Emergency cut-off conversion saddle 71 is in the position according to Fig. 1, this is because emergency cut-off solenoid valve 72 is motivated.
As long as also needing to maintain the positioning of hydraulic cylinder 6, the pilot solenoid valve 91 that is controled by the adjuster of hydrodynamic machine, 92 are just in de-energized state.So that leading to the energy in the opening side of hydraulic cylinder 6 or the control route of close side It releases what the check-valves 81,82 ended was also closed, and is maintained at hydraulic cylinder 6 in its positioning.In this state, turn The variable driver 3 of speed is turned off, and is introduced in system from without consuming energy (heat).Thus, however, it would be possible to cancel The advantages of cooling to oil, this provides obvious better efficiency.
If needing adjustment process (such as target value variation or adjusting deviation amount have been more than specific value (dead zone)) now, So pilot valve 91 and 92 is just motivated via adjuster, this causes the check-valves that can release cut-off to be opened.Now, hydraulic cylinder can Directly to be positioned via the pump controller of variable speed 3.If hydraulic cylinder 6 is manufactured into synchronized cylinder, by pump assembly 2 from It draws the oil mass swallowed of side just and is on the pressure side introduced in cylinder oil mass as many.In this case, two pumps of pump assembly 2 With consistent delivered volume amount.If the manufacture of hydraulic cylinder 6 is at cylinder with differential effect, the delivered volume amount of two pumps of pump assembly 2 Ratio will match with cylinder with differential effect as far as possible.The difference oil mass generated during hydraulic cylinder 6 is mobile can be via correspondingly coupling It is compensated collecting and compensating absorption route or small oscillation volume on memory 5 on container 1.Configuration referring to Fig.1, For this purpose, the pump volume of the pump of top can be designed than required greatlyyer, this is because the extra amount of hydraulic fluid is hydraulic Cylinder 6 is pressed into memory when closing via check-valves 14.In another rotation direction of axis, extra amount by collect and Container 1 is compensated to provide and be received again.It is clear that each fortune in hydraulic cylinder 6 in the closing direction in this way All memory 5 is charged when dynamic.It is additional by (being not shown in Fig. 1) pressure override valve or via what be there can optionally be Customer (interface 40) can prevent memory 5 from excessively being charged.
After reaching desired positioning, pilot valve 91,92 is released from excitation, is being applied cylinder 6 not again It is maintained in the case where energy in its positioning.It is to be noted that comparing traditional system, memory size is no longer used to adjust for Purpose, this is because the task is undertaken by pump assembly 2 completely.Therefore, memory size and memory ruler can be greatly reduced It is very little.This has also additionally resulted in smaller collection and compensation container 1, thus generally can reduce cost.
It is influenced to protect equipment not by the high pressure not allowed, installation limited valve 30,31 is optionally able to, wherein respectively One pressure limiting valve be attached to wherein one can release cut-off check-valves (81,81) and emergency cut-off convert saddle (71) between Route.
Emergency cut-off:
In order to ensure hydrodynamic machine safe shutdown in faulty situation, emergency closing function is applied, this is urgent Closing function makes facility stop fortune in the case where no electric current is supplied (or when the driver 3 of variable speed is problematic) Turn.In emergency cut-off, excitation is released from by the emergency cut-off solenoid valve 72 of persistent excitation in operation, then, promptly Conversion saddle 71 is closed to be pushed in the position different from shown in Fig. 1.Therefore, hydraulic from " being closure to a certain extent " Regulating loop becomes open circuit.Memory 5 is connect with the close side of hydraulic cylinder 6, wherein opening side is turned to by control now Into collection and compensation container 1.Simultaneously, the pressure for leading to pilot valve 91,92 is removed load, thus enabled releasing cut-off Check-valves 81,82 is closed.
In the circuit of the opening, memory 5 provides the volume of the restriction within the pressure limit of restriction.It therefore can With by basic throttling element 10 and additionally concatenated throttling element 11 or 12 reliably regulates and controls the shut-in time of restriction.If practical On used two additionally concatenated throttling elements 11 and 12, then saddle 71 and deposit thus relative to for example being converted in emergency cut-off Occurring the case where rupture of line in route between reservoir 1 obtains greater flexibility and bigger stability, this is because Additional restriction effect is assigned on two throttling elements, and only one of them (12) fails because of rupture of line.
When hydraulic cylinder 6 is mobile, the back pressure to work against pump assembly 2 is generated by basic throttling element 10, and should Therefore back pressure preferably must be held in certain limit and (follow nominal pressure, power of pump controller 3 of route and part etc.). Therefore, it is necessary to individually be designed each throttling element 10,11,12.It is herein most of all, total via basic throttling element 10 It is the shut-in time that must be realized total restriction effect of maximum possible accounting, and then realize maximum possible accounting.It is one of former Because being, by the way that basic throttling element 10 to be directly arranged in the opening side of hydraulic cylinder 6, so that even if for example opening control side (that is route between basic throttling element 10 and pump assembly 2) occurs to still ensure that the limit to the shut-in time when rupture of line System.
Since memory 5 is connect via the route with check-valves 14 with the close side of cylinder 6, so that even there is pump driving In the case where the failure for the maximum (top) speed that the hypothesis of device 3 has had more than the restriction in closing direction, also limited via basic throttling element 10 The execution time is made.Only the pressure in memory 5 is slowly improved due to pumping the raising of conveying capacity.
Memory charges function:
Memory 5 is by corresponding horizontal and its compactedness of pressure monitor sensor or its system pressure.In operation, nothing By hydraulic cylinder 6 position how, oil volume and pressure in memory 5 are held in the highest level of restriction.Using same It (is seen above) in the case where step cylinder in other words when the customer of not other outside is via optional connection position 40 and storage When device 5 couples, which does not change in operation or only very little changes.
However, memory can be by the drive of variable speed in order to also be able to use the customer of cylinder with differential effect and outside It moves device 3 and is independently filled with the position of hydraulic cylinder 6 during operation through the check-valves 81 and 82 that can release cut-off that electricity controls It carries.
For this purpose, pilot solenoid valve 91 and 92 must be in de-energized state, stopping for cut-off can be released as a result, by also allowing Valve 81 and 82 is returned to close.Pump assembly 2 is controled now, so that the direction progress of the pump assembly towards the close side of hydraulic cylinder 6 is defeated It send.Thus the positioning of cylinder 6 does not change, this is because can release the check-valves 81 of cut-off is in the opening side of hydraulic cylinder 6 It closes, and does not therefore have oil and overflowed from hydraulic cylinder 6.But check-valves 82 is flow pass through in the closing direction, thus So that pressure improves, and charge memory 5 via the route with check-valves 14.Difference oil mass needed for thus is pumped Component 2 is drawn via corresponding route from collecting and compensating container 1.If route with check-valves 14 with from pump assembly 2 Towards the route connection of the opening side of hydraulic cylinder 6, then charges and similarly act on.But pump assembly 2 must be controled thus, so that the pump Component is conveyed on the direction of the opening side of hydraulic cylinder 6.
If should need adjustment process during charging, the adjustment process is prior to charging process.From safe skill This is not problem from the viewpoint of art, this is because horizontal and pressure monitor corresponding switching point ensures, possible tight Under anxious closing situation, always there are enough volumes or pressure in memory.It can by the excitation and revolving speed of pilot valve 91 and 92 The driver 3 of change controls, and can be again carried out adjusting movement immediately.
Memory charge function hydrodynamic machine during normal operation be during shutdown activation.It is ensured that It is always possible emergency cut-off situation and provides corresponding safety guarantee, and can be as fast as possible in hydrodynamic machine starting Corresponding safety guarantee is provided fastly for using.
Optional quick closedown function:
In general, pump assembly 2 is designed in terms of the size of pump, revolving speed and power, so that only via pump controller 3 It can realize the opening and closing time for hydraulic cylinder 6 required for each application.
When for example there is big hydraulic cylinder accumulated amount and compared with the shut-in time opening time need it is considerably longer, so as to When the specification of pump assembly 2 and pump controller 3 being allowed to be kept as small (special case, refill-unit cost etc.) as far as possible, pump assembly and Pump controller is designed to, so that only being capable of mobile hydraulic cylinder 6 with least opening time.
It, can in order to then realize faster shut-in time (such as during off-load using hydraulic regulator) Selection of land is provided with quick closedown solenoid valve 20, is located in the underground at 72 place of emergency cut-off solenoid valve.It should by connecting Valve 20, it now is possible to be closed using memory size.Here, quick closedown solenoid valve 20 is motivated, so that promptly Conversion saddle 71 is closed to be pushed to different from position shown in Fig. 1.It is hydraulic by the quick closedown solenoid valve simultaneously The pressure transport for leading to pilot valve 91 and 92 has been isolated in ground, can release the check-valves 81 and 82 ended to allow and control in route It is also switched off.Therefore pump assembly 2 takes off connection with hydraulic cylinder 6 completely.
In order to for example have a possibility that capable of making machine synchronous again after off-load in the case where water turbine, reaching To restriction disconnection when, quick closing valve 20 is by de-energized again.At the same time, it " fine-tunes " now and is transferred to and turn The variable pump controller 3 of speed, and be synchronized machine can again.
Because having emptied memory 5 by quick closedown, should fill as quickly as possible in this case Memory 5.Because being pushed to corresponding cylinder again after terminating during synchronizing process with synchronizing process and in turbine When on position, adjuster is activation, and thus pump assembly 2 should not be used to charge memory 5, so this In the case of can take following way:
During hydraulic cylinder 6 is pushed to corresponding open by pump assembly 2, pilot solenoid valve 91 and 92 is in de-energized In state.Therefore, the check-valves 82 of opening side can be flow pass through, and the check-valves 91 of close side then keeps being ended.Thus The oil being pushed out away when being pushed is squeezed via the route with check-valves 14 from hydraulic cylinder 6 to be pressed back into memory 5. Oil mass needed for thus is drawn via corresponding route from collecting and compensating container 1 by pump assembly 2.If memory 5 reaches it Nominal compactedness, then corresponding check-valves 81 and 82 is turned on, and hydraulic cylinder 6 can not continue to fill up memory 5 In the case where migrate in its final positioning.
Heating function:
When lower than the oil temperature limited, caused via pump assembly 2 by opening the check-valves 81 and 82 that can be released and end It adjusts.Thereby produce the heat for being used for heating system.

Claims (8)

1. the equipment for adjusting hydrodynamic machine, the equipment include: pump assembly (2), the pump controller (3) of variable speed, deposit Reservoir (5), hydraulic cylinder (6), two can release cut-off check-valves (81,82) and for make the check-valves (81,82) release Two pilot valves (91,92) of cut-off, wherein the pump assembly (2) includes two pumps with reversible conveying direction, described Pump is connect with the pump controller (3) of the variable speed, and the pump is driven on two conveying directions by the pump Dynamic device (3) drive, which is characterized in that the equipment further include collect and compensation container (1), emergency cut-off solenoid valve (72), Saddle (71), check-valves (14) and at least two throttling elements (10,11,12) are converted in emergency cut-off, wherein the emergency cut-off turns Change saddle (71) and the pump assembly (2), the hydraulic cylinder (6), the collection and compensation container (1) and the memory (5) connect and show as so that the emergency cut-off conversion saddle (71) first position in, first pump first interface with The opening side of the hydraulic cylinder (6) connects, and the first interface of the second pump is connect with the close side of the hydraulic cylinder, and is made Memory (5) and the hydraulic cylinder (6) and collection and compensation container (1) and the de- connection of the hydraulic cylinder, and in the emergency cut-off In the second position for converting saddle (71), the collection and compensation container (1) are connect with the opening side of the hydraulic cylinder (6), and And the memory (5) connect with the close side of the hydraulic cylinder, and keeps the pump assembly (2) and the hydraulic cylinder (6) de- Connection, and wherein, in addition, remaining interface of pump is connect with the collection and compensation container (1) respectively, to drive in the pump On the driving direction of dynamic device (3), first pump can be by hydraulic fluid from the collection and compensation container (1) to described hydraulic Cylinder (6) direction conveying, and it is described second pump can by hydraulic fluid from the hydraulic cylinder (6) that side be transported to it is described collection and It compensates in container (1), and wherein, respectively there is the check-valves (81,82) that can release cut-off to be located therein one from pump to liquid In the route of cylinder pressure (6), and it is oriented such that under any state of the check-valves (81,82), hydraulic fluid can It is current on the direction towards the hydraulic cylinder (6), and the equipment furthermore include by the memory (5) respectively with it is described The route that two check-valves (81,82) and emergency cut-off conversion saddle (71) connect, so as to make the non-return Valve (81,82) releases cut-off and saddle (71) can be converted in the emergency cut-off and is maintained in the first position, wherein The route at least forms unique route via the part for being wherein disposed with the emergency cut-off solenoid valve (72), so as in liquid It is permanently excited during power facility operation and is perforation in this position, and wherein, the pilot valve (91,92) point It is not arranged in the part for separating extension of the route between the memory (5) and the check-valves (81,82), and with energy The mode that electricity controls is constituted, and wherein, has a throttling element (10) to be located at the route for leading to the opening side of the hydraulic cylinder (6) In, thus the hydraulic cylinder (6) it is each movement in by hydraulic fluid percolation and mistake, and another throttling element (11,12) or In route between the collection and compensation container (1) and emergency cut-off conversion saddle (71) or it is located at described In route between memory (5) and emergency cut-off conversion saddle (71), and wherein, the check-valves (14) is arranged in In the route that wherein one is connected from pump assembly (2) to the route of hydraulic cylinder (6) and the memory (5), so that not having There is the hydraulic fluid from the memory (5) check-valves (14) can be passed through.
2. equipment according to claim 1, which is characterized in that the equipment include it is other otherwise be located at it is described collection and Compensate container (1) and the emergency cut-off conversion saddle (71) between route in otherwise positioned at the memory (5) with it is described The throttling element (11,12) in the route between saddle (71) is converted in emergency cut-off.
3. equipment according to claim 1 or 2, which is characterized in that the equipment includes two pressure limiting valves (30,31), In respectively have a pressure limiting valve be attached to wherein one it is described can release cut-off check-valves (81,82) and the emergency cut-off turn Change the route between saddle (71).
4. equipment according to any one of claim 1 to 3, which is characterized in that the equipment includes the electricity that electric can be controled Magnet valve (20), the solenoid valve that electric can be controled and the emergency cut-off solenoid valve (72) are arranged in same route, and structure Cause to enable its emergency cut-off conversion saddle (71) is moved in the second position when being electrically excited and It can allow the pilot valve (91,92) and the memory (5) are de- to join.
5. equipment according to any one of claim 1 to 4, which is characterized in that the equipment includes for other tight It is anxious close valve, be arranged in same route with the emergency cut-off solenoid valve (72) and couple position (50).
6. equipment according to any one of claim 1 to 5, which is characterized in that the equipment includes for other liquid Press liquid customer, be arranged in from the memory (5) lead to the emergency cut-off conversion saddle (71) route in connection Socket part position (40).
7. equipment according to any one of claim 1 to 6, which is characterized in that hydraulic cylinder (6) manufacture is at synchronization Cylinder, and the pump of the pump assembly (2) often transfers and send same amount of hydraulic fluid.
8. equipment according to any one of claim 1 to 6, which is characterized in that hydraulic cylinder (6) manufacture is at differential Cylinder, and the pump of the pump assembly (2) often transfers and send different amounts of hydraulic fluid, wherein conveying capacity ratio and the hydraulic cylinder (6) match in the volume ratio of close side and opening side.
CN201880021394.5A 2017-03-29 2018-02-08 Device for regulating a hydraulic machine Active CN110520634B (en)

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DE102017106700.0A DE102017106700B3 (en) 2017-03-29 2017-03-29 Device for controlling a hydraulic machine
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FR3123312B1 (en) * 2021-05-28 2024-01-12 Safran Aircraft Engines Feathering of the electrohydraulic system with pump by valves in the rotating mark
DE102022121962A1 (en) * 2022-08-31 2024-02-29 Bucher Hydraulics Ag Electric-hydraulic actuator

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US20200096015A1 (en) 2020-03-26
CA3058355A1 (en) 2018-10-04
WO2018177641A1 (en) 2018-10-04
EP3601806A1 (en) 2020-02-05
CN110520634B (en) 2020-09-04
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CA3058355C (en) 2024-05-07
US10962032B2 (en) 2021-03-30

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